Machine tool



May 5, 1936. c. H. 'HOWLAND-SHEARM'AN 9 3 MACHINE TOOL Filed July 27, 1954 11 Sheets-Sheet 1 NVENTOR 014mm #HOWLAND-WRMN ATTORNEY My 5, 1936- c. H. HOWLAND-SHEARMAN 2,039,842

MACHINE TOOL Filed July 27, 1934 ll Sheets-Sheet 2 ATTORNEY May 5, 1936, c. H. HOWLAND-SHEARMAN 4 MACHINE TOOL Filed July 27, 1934 11 Sheets-Sheet 4 ATTORNEY May 5, 1936.

c. H. 'HOWLAND-SHEARMAN MACHINE TOOL Filed July 27, 1934 ll Sheets-Sheet 5 Nam low

I N V E N TO R CHARLES ii HOWZMD-5IIE4YRHEN ATTORNEY May s, 1936;

C. H. HOWLAND-SHEARMAN MACHINE TOOL Filed July 27, 1954 11 Sheets-Sheet 6 MH H INVENTOR amzzisflllomm-fimmv u May 5, 1936.

c H. HOWLAND-SHEARMAN MACHINE TOOL Filed July 27, 1934 ll Sheets-Sheet 7 m INVENTOR 014191356 HF0MfiW-5'EEHRM1YN A'ITORNF' y c. H. HOWLAND-SHEARMAN MACHINE TOOL Filed July 27, 1934 ll Sheets-Sheet 9 VEZOC/TV RE5/5 TflNCE INVENTOR ma mas Eflowamm -51/M121Y9N ATTORNEY May 5, 1936. c. H. HOWLAND-SHEARMAN 2,039,342

MACHINE TOOL Filed July 27, .1934 ll Sheets-Sheet l0 1 Am. nwwm guy/[mun w? I 4 EN-r ATTORNEY y 9 c. H. HOWLAND-SHEARMAN 2,039,842

MACHINE TOOL Filed July 27, 1954, 11 sheets-Sheet 11 'INVENTOR 0141MB 19? Join 11w, -.9'11rx/m1v ATTORNEY HI HLM [UNITEDSTATES' PATEN OFFICE TOOL 1 M n. mum-slim Hamden, am. sit atio July :1, 1924, Serial No. 131,1.

140mm. (mm-so)" This invention relates to apparatus for cold-.

- working materials. In mplication; Serial No. 702,286 is described'and claimed a method of 'flprodmucing cold flow in certain types of mate- 20 'Figure 6 illustrates the mechanism for pulsating the table. I

Figurelisadetailsectionofpartofthesprin motor adjusting means. Figure 8 is a sectional view of the dash pot.- Figure 9 is a transverse section showing the flywheel, gearing and power shaft assembly.

Figure ,10 is section of the same in the plane Ill-l0, Figure 9.

Figure 11 is a detail view of the micrometer crank transfer gearing. I

Figure 12 illustrates the high pressure linkage at the beginning of the ram work stroke. Figure 13 illustrates the same at the end of the work stroke.

4 Figure 14 is an enlarged view of the workhead and-fracture proofer.

Figure 15 is a; transverse sectional view in the plane |I|S, Figure 12. Figure 16 is a .transverse section in the plane lt-u, Figure 12.

, Figure 1': is a sectional view oft-he clutch.

Figurel8isasimilarviewoftheflexiblereducingdrive mechanism. I- I Figure,,l9 is a diagram illustrating the speed, pressure and movement during cold flow as produced by-the present invention.

In order to set forth clearly the prime -func-- tions of the apparatus provided for carrying out the method set forth and claimedin the above named application, atypical example of cold flow is described as follows, in"conn'ection with diagrammatic Figures 1, 2, and'3: j

A work piece 20, assumed to be a steeleplate from which it is desired to flow a cylindricafiflw, I 55 is placed on a supporting rest plate 2|. a

cylindrical tool 22 having a diameter equal to the desired plug. The rest plate 2| contains a hole 23 axially allned with'the tool 22 and having a diameter greater than the tool by a slight clearance of the order 01".0002 inch. Surround- 5 ing the tool 22 which is slidably fitted therein is a clamping member or fracture prooter 24.

An initial upward pressure is first applied by. the rest plate 2| to the work piece 20. This pressure is transmitted through the work piece 2| to th'e fracture proofer 24 and to the tool 22' which resist the pressure. That portion or the work piece which is between the rest plate 2| and fracture proofer 24 is held rigidly in compression, while that portion 25 under the tool 22 exerts an upward pressure against the latter. v r

A relatively large pressureis now applied downward' by the tool, starting from rest with very low initial speed. It has been determined that the typical. structure of steel is an aggregate of crystalline particles, indicated by the numeral 28, Figures 1 and 2, suspended in-and cemented together by amorphous material or flux 21. It has furthermore been determined that when steel is stressed beyond its elastic limit the change from elastic to a plastic or'yielding state occurs suddenly, marking a sharp or instantaneous point in the pressure transit. -When the downward or worflnlpressure is applied by the tool 22 to the portion 25 which is not directly supported by the rest plate 2| and fracture proofer 24, the entire .working pressure is resisted by the cylindrical none 2| of microscopic thickness forming the boundary of the portion 25. As the working pressure is built up rapidly but without suiiicient 5' tool movement to cause ordinaryrupture, the material inthe entire zone'll suddenly changes from the elastic-to'the plastic state. 'l'he crystals 2. flow through the amorphous matar 2i which acts as a flux and the portion 2| under 40 increaling'speed and movement of the tool is I eiectedthroughthehole 23. Duringthe flowtbe originallyformingapartoitheaone'or crystals slip plane 28 are forced or compacted into the of'the plug and hole and the amorphous matter is swept along the cylindrical plane, ap-

pearing in theflnlshed hole and on the finished plug as minute striationsparailel to the direction of force application.

Ithasfurtherbeendeterminedthatthepres msure resistance to yield in steel stressed beyond its elastic limit falls oil in parabolic-relationship appliedpressure and pressureare-alwaysequal,andasspeeds out a mechanical linkage, it is evident that the tool 22 must be, caused to apply its pressure to the portion 25at speed increasing in parabolic relation to its increase of travel in order to follow accurately the natural yield of the material and produce cold flow. In other words, too great a speed would cause fracture rather than flow, while too slow a tool motion would cause lagand jerk, similarly giving rough and inaccurate part ing. The tool 22 in the present invention is pressure is to be applied and to apply the working pressure thereto which causes the phenomenon of cold flow. v

Figure 4 is a general view of a machine, hereinafter referred to asthe Kinetor, adapted to carry out the process described above. In order to set forth clearly the manner in which the functions of the machine are performed, the principal functions will first be taken up individually in describing the particular structures which perform them.

The principal functions necessary to the process described are as follows:

1. Application of upward pre-pressure.

' 2. Application of downward working pressure.

3. Fracture-proofing. Fracture proofing must accompany the entire application of working pressure and is initiated by the upward pre-pressure which is also applied to the tool and which is therefore the first essential to the process. This pre-pressure issupplied by a pulsating table mechanism of the type fully described in co-pending application Serial No. 737,157 and hereinafter explained in its embodiment in the present invention.

Pulsating table mechanism 5 and 6 show the construction of the above mechanism. Referring to Figure 5, the rest plate 2| is seen to be supported in a bolster 23. In this embodiment the plate2l has an insert 33 containing the hole 23. The bolster 23 is-secured to a table 3| having an inclined lower surface 32 bearing on a hollow slidable wedge 33 which in'turn is supported on the base 34 of the machine. The table 3| is guided vertically by stationary rails 35 attached to the base 34. A manually reciprocable knockout rod 333 is provided to facilitate removal of the rest plate 2| from the bolster 23.

Attached to the wedge 33 is a heavy 'rod 33 having a, long worm thread 31 on which is screwed a sleeve member 33 rotatably and slidably mounted in a guide 39 attached to supporting side plates 43 and 43a which are secured to the base the sleeve 33 by means of a screwed collar 42, the sleeve 33 and collar 42 being rotatable in the shoe 4|.

A second wedge 43 is dovetailed in vertically sliding relation to the shoe 4|, and is also slidably dovetailed to an inclined stationary backing member 44. The lower end of the wedge A' shoe 4| is retained on the right end of 43 is articulated by means of a pin 45 to a toggle 43 comprising upper and lower arms 41 and 48 jointed together on a pin 43. The lower arm 43 is secured to a pin 53 rotatably anchored in the base 34. A link 5| and pin 5|a connect the central toggle pin 43 to a bell cranklever 52 fulcrumed on a stationary-pin 53 and having a substantially horizontal arm 54 extending toward the rear of the machine.

It will be seen that a counter-clockwise swing of the .bell crank 52 operates the toggle 43 to raise the wedge43, force the shoe 4|, cylindrical member 33, rod 33 and wedge 33 to the left, and thus raise the table 3|. Similarly a clockwise movement of the bell crank 52' draws down the wedge 43, and as 43 is dovetailed to both the backing member-44 and the shoe 4|, the wedge 33 is positively withdrawn, allowing the table 3| to move downward by gravity to its lower position as shown.

The sleeve 33 carries a bevel gear wheel 55 which may be revolved by a mating bevel gear 335 operable by an exterior hand wheel 32|, Figure 4, to screw the rod 33 to the right or left and thus effect an initial vertical adjustment of the table 3|.

As shown in Figure 6, the arm 54 of the bell crank 52 is connected by a short oscillating link 53 to a plunger 51 which is slidable vertically in a stationary cylinder 53 formed integrally with or secured to the base 34. vA vertical rod 59, fastened to the plunger 51, extends concentrically through the cylinder 53 and is connected by a short oscillating link 33 with a walking beam 3| fulcrumed on cross pin or shaft 32. A flanged sleeve 33 having attached thereto a bevel gear 34,- having a meshing bevel gear 322 operable by retained in a stepped bushing 35 screwed into the lower end of the cylinder 53, and surrounds the rod 53. The sleeve 33 is formed with a hex: agonal exterior 33 slidably engaging a hexagonal hole 31 in a nut 33 which is threaded into the cylinder 53. By turning the gear 34 and withsprings 1| and 12 may be varied by adjusting the nut 33" upward or downward in the cylinder 53' as previously explained, the bearing 39 preventing torsion of the springs during adjustment. The plate 13 has an indicating ,flnger 15 protruding through a slot 13, Figure 1, so as to register with an exterior visual scale 11 graduated to correspond with the calibrated strengths of springs 1|, 12, and 13.

The rearwardly extending arm 13 of the walking beam 3| is articulated on a pin 13 fastened to a yoke 33 which spans a beam 3|, hereinafter referred to as the micrometer beam. Circular slots 32 in the beam 3| contain slidable segments 33 which are pivoted on pins 34 fixed in a nut 35. The pins. are also pivotally engaged by the yoke 33. The nut 35 is disposed on a micrometer screw 33 rotatably retained in a sleeve 31 trunnioned in the rear end 33 of the beam 3|. An exterior hand wheel 33, Figure 1, is provided on the screw 33. n V

- an exterior hand wheel 323, Figure 4, is rotatably aosaadsi The beam'li s'wingson a stationary cross pin ll and is centrally connected by meansofanoscillatinglinklltoarelease plunger ll slidablevertically in a stationary guide ll. A lift plung r ll isslidable vertical y in therelease plunger ll and is .connectedby a rodli and pivotpin ll to aneccentric strap l'l. Thestrap ll engages an eccentric ll securedtotbedrivenmemberllofaclutchdis-.

extension 3 of the micrometer beamlI.

'40 The latch II! is thereby withdrawn from the thebasellasshowninI-igure1andcarries'a a stationary Starting from the-position shown in Figure 6, the eccentric ll is revolved by the driven member ll. The lift-plunger O4 is drawn upward- As the latch Ill is in thenotch IlI the rise of the lift plunger carries with it the release plunger ll, swings the micrometer beam lI counterclockwise, raises the yoke ll,,and acting through thewalkingbeamllandrod59,drawsthe plunger 51 downward, thus compressing the springs II, II, and Il. At the same time the bell crank it is swung clockwise, drawing out the toggle ll and retracting the wedge ll to lower thetablell asshowninli'igureiv.

As thelift plunger ll approaches its top position the counter-clockwise swing of the microm-.

eterbeam ll cau'sesthetripblockllltoengage.

the block lll, swingin the lever III to the left.

notch IlI, releasing the plunger ll and its attached linkage. The springs II, I2, and Il expand, forcing up the plunger 51, rocking the bell crank 52 counter-clockwise. straightening the toggle'll' and raising the table II with a pressure determined by the setting of the springs multiplied by the combined mechanical advantages o! the toggle and both wedges. As these mechanical advantages are fixed it is evident that the upward table pressure is determined directly by the compressive setting of the springs II, I2, and Il. For this reason the scale 11 may he graduated directly interms of table pressure.

By moving the segments ll along the slots ll nearer to or farther from the fulcrum ll of the micrometer beam lI by means of the micrometer screw ll, the amplitude of motion transmitted .to the walking beam lI and hence the amplitude of table pulsatlon'may-be varied. The slots l2... are cut on a radius struck from thecenter of pin ll when the'parts arein the position shownin" l'lgure 8, hence no alteration of initial or lower I position of the beam ll and consequentlythe table ll is effected by moving the ts ll. The pin ll protrudw through a slot lit in dial lll adaptedinlower position to register with segmentsllbeingadirectmeasureofthetabie I I is calibrated directly in term of amplitudeof table In the operation deserlbed the Ill'was withdrawn to trip the automatically byengagementof-thetripblocklllandblock micrometer beam ll.

pointer ll. The position Of Ill. In case it is desired to operate the trip manually the following provision is made:

The block Ill is slidable vertically in the lever III. A- link I" connects the block Ill with a short lever Ill fastened to the cross shaft Ill.

A second short lever IIl on sbaft'Ill carries a pin Ill engaging a slot III in adouble ended lever III which is connected by a link Ill to a swing nl lever Ill as shown more clearly in Figurell. An operating rod I II is articulated to the lever Ill. -When the lever Ill is swung counterclockwise by means of the rod 12s, the shaft m is also rocked counter-clockwise, and the lever Ill and link I" move the block Ill upward, until 'a notch Ill formed therein comes opposite the trip block -I II. When the trip block. now moves to the left it enters the notch Ill instead of encountering the block Ill. As a result the lever Ill is. not actuated to withdraw the latch Ill, which thus remains engaged.

guide ll is a manual trip block Ill movable by a slottedlever Ill fastened to a rockable shaft Ill. The block I21 contains a downwardly spring-presed plunger Ill adapted to engage a therefore, the release plunger 92 nears the top of its stroke the plunger Ill engages the slot Ill. If the shaft III is now turned clockwise by manual-means hereinafter described, the lever Ill moves the block Ill and latch Ill to the left,

withdrawing the latter from the notch Ill. The mechanism is thus tripped and the table given itsupward pulsationas previously de- The release plunger 92 is provided with a stop cushion Ill of raw hide or other'suitable -material secured to thebase ll. The motion of the. parts after tripping may also be cushioned by an adjustable dash pot Ill, Figure 8, actuated through a walking beam Ill-and link Ill by the The downward or working pressure is applied by power derived from the power. shaft Ill through a clutch Ill, Figure 9, hereinafter described in ,preferred form, a micrometer crank mechanism Illa of the type fully described in co-pending application Serial No. 737,158 and a combination of elements hereinafter described and referred to as the high pressure linkage.

Micrometer crank mechanism Secured to the outer or hub end or the driven member ll of the clutch Ill by means of integral cross keysj Ill and locating bolts Ill is a crank body Ill. A block Ill carrying a crank pin Ill is'slidably retainedin stepped ways I42 in the body Ill and is movableby means of a micrometer screw Ill rotatably retained therein. The

right end of screw Ill carries a spur gear Ill imeshing with a pinion I45 on a stub shaft Ill Slidably dovetailed to the top of the stationary notch m iii-the top of the latch 102. when,

rotatably mounted in the end of body m and equipped with a manual adjusting wheel Ill.

' By turning the wheel I4] the block Ill and crank pin ill the center line may be moved nearer to or farther from of the-shaft Ill, thus varying the throw of the crank. A pointer Ill on the block Ill registers with a scale Ill on the body Ill. As the stroke of the tool 22 is governed by the length of crank throw, the scale Illis calibrated directly in terms of tool stroke.

Rotatably titted on the crank pin MI is a connectingrod Ill having a body Ill formed with internal longitudinal ways Ill-in which ablock Ill is moveable by means of a second screw Ill when the gears are alined as noted above.

roiatably retained in II and having a lead identical with that of the micrometer screw I43, but of opposite thread. A wide spur gear 'I55 is fastened to the screw I54 in such a position that when the crank and connecting rod are at right dead center as inFigure 4, the gear I55 is located in line with a similar gear I56 on the micrometer screw I43. An idler gear, I51 on an arm I58 swung about the micrometer screw I43 and meshed with the gear I56 may be swung intomesh with the gear I55 as illustrated in Figure 11 A locating pin or button I59 in the arm I58 is adapted to engage holes I68 and IGI to hold the idler gear I51 in meshed or free position respectively.

The block I53 carries a wrist pin I62 which engages a lever I63 fixed by means of a heavy shear pin H531: to a cross shaft I64 journalled in the side plates 48 and 4811. With the parts in left dead center position as shown in Figure 1, and with the idler or transfer gear I51 in mesh, rotation of the micrometer screw I43 causes a similar rotation of the screw I54. The screws being of opposite thread and of the same lead, as the crank pin I is moved relative to the shaft center, carrying with it the connecting rod I58, the block I 53 and wrist pin I62 are moved the same distance in the opposite direction relative to the connecting rod body I5I. Thus the eifective length of the connecting rod is changed to compensate for the change in crank throw, the wrist pin I62 and lever I63 retaining their initial positions without change.

The crank throw having been adjusted, the transfer gear I51 is thrown out of mesh.

High pressure linkage length as 7 I61 is articulated to the latter by a pin I18. The left end of arm I69 is jointed by means of a pin "I to the middle portion of a substantially vertical lever I12 swung on a cross p'n I13 secured to the side plates 48 and 4811. When the device is in normal position as shown in Figure 12 the pins I68. I19, and -I1I lie in a straight line, fulfilling with the arms I51 and I69 physical definition of an infinite plane. This combination of pins and arms constitutes a tractor lever lfiec hereinafter referred to as the secondary tractor lever. v

' A walking beam I14, trunnioned to the base 34 and connected to the pin I18 by a link3II5, carries a counter-weight I16 which balances the weight of the arms I61 and I69, thus relieving the 57 teeth of segments I65 and I56 of all strain except that imposed by the working force transmitted through them.

' The lower end of lever I 12 carries a pin I11 which is connected by a link I18 to the central pin I19 of a primary tractor lever I88 comprising upper and lcwer arm I8I and I82. The lower arm I82 is anchored on a pivot I83 secured in'the side plates 48 and 40a. The upper arm I8I is secured to a pin I84 journalled in a massive tool beam I85, the 'pins I19; I33 and I84 normally being alined to form a primary infinite plane. Rotatably retained in the right or rear end of the beam I85 is an eccentric bushing I86 which is rotatably mounted on .a stationary anchor pin m. A ram I88, slidable vertically in a guide us shown in enlarged section in Figure 14.

secured to the side plates 48 and 48a, is secured to a heavy pin I98 pivotally journalled in the left or front end of the beam I 85. A flanged cylindrical member I9I forming the lower portion of the ram I88 has a tool holder I92 socketed therein and secured by a tapered cross key I93 as The tool holder I92 may be adapted to carry a plurality of tools of any desired shape, but in the present illustration holds a single cylindrical tool I 94 held in place by a screw thread I95.

The manner in which the power derived from the shaft I88 is transferred through the high pressure linkage to the tool I94 and work piece is as follows:

. When the crank pin I is at right hand dead center the primary and secondary tractor levers are in their straight or infinite plane positions and the tool I94 is at the topof its stroke as shown in Figure 12. The alinement of the tractor levers is assured by the application of upward pre-pressure through the work piece to the tool I94 by a pulsation of the table 3I as previously described. This upward pressure tends to raise the beam I85, placing both tractor'levers under initial tension which brings their respective end and center pins into correct alinement as stated. At the same time any lost motion which may have developed in the linkage due to wear is taken up. 7

Referring to Figure 12, the crank pin I now moves counter-clockwise from right dead center. The arm I63 and cross shaft I64 are thereby rocked clockwise. The segment I65 moves the meshing segment I66 downward, swinging the lever I61 about the anchor pin I68. The secondary tractor lever I690 is thus forced out of its alined or infinite plane position, drawing the pin HI and vertical lever I 12 to the right, causing the link I18 to push the central pivot I19 of the primary tractor lever I88 to the right. As the lower arm I82 is pivotally-anchored to the base 34, the

"pull of the primary tractor lever draws the pin I84 downward rocking the beam I85. The ram I88 moves downwardv in the guide I89 to'force the tool .22 through the work piece28 as shown in Figure 13 flowing out the plug 25, Figure 3.

The crank pin I4I revolves past left dead center and continues on to right dead center, withdrawing the tool 22 from the. work andrestoring the parts to their'initial position as shown in Figure 12.

In the description of the process of cold flow it has been set forth that the natural resistance to flow of the material decreases in parabolic proportion to the increase of yield. The tool producing the flow must supply the pressure necessary to overcome the resistance and must travel at such speed as to exactly keep pace with the natural yield.

.The characteristic action of a tractor lever is the exact opposite of a toggle, that is, as the former is actuated it exercises a mechanical advantage starting at infinity at the instant of departure from the infinite plane and decreasing in falling proportioned that their compoimd action moves thetool gam a with a velocity increasing in Y tions between these properties.

in the present invention, which magnitudes.

versely,-the tool pressure for a given power decreases in parabolic relation to the tool travel.

The tool therefore is actuated in the manner that no 10st motion remains and that the tractor levers are fully extended, the tool moves downward from rest and with ,very slight motion quickly applies sufiicient pressure to overcome the elasticity of the material which yields and flows as described, the tool speeding up to keep pace, with the yield and supply the working pressure until flow is complete.

With some materials the flow is completed and the plug completely severed during the early stages of the stroke, the remainder of the stroke serving to eject the plug.

Referring to diagram, Figure 19, it should noted that the values plotted do not represent absolute velocities, pressures, etc., but purely rela- In other words, the production of cold flow depends on the maintenance of proper relationship between pressures, speeds and travel rather than on their absolute The ability to maintain the above proper relationship within its range is inherent is therefore adaptable to a wide variety of speeds and materials, and may be constructed in any desired size so long as the proper proportions of the high pressure linkage are followed.

In a preferred form as reduced to practice, the following data are given as illustrating a proper proportioning of the parts:

1,500,000 lbs.

Angularity of primary tractor lever at end of if; inch tool stroke"; Angularity of secondary tractor lever Combined kinetic efliciency or mechanical advantage of tractor lever linkage and tool beam at end of 1 inch tool stroke";

1 From the above it will be noted that themechanical advantage drops from 58.308 to 1.728. 'Ihe.speed ratio, being the inverse of the mechanical advantage, rises correspondingly. If the values of mechanical advantage and velocity ratio are plotted for corresponding increments of tool advance between t e two ex e es oted, the

istics illustrated in Figure 19.

Fracture proofer The function oi. fracture proofing, that is maintaining the structure of material surrounding the work area intact during the work stroke, may be performed by a device of the type fully described in co-pending application Serial No. 737,156, and herein described as follows, referring to Figure 14: V

- result is a pair of curves following the character Slidably guided on the lower cylindrical portion I86 of the lower ram member I8I is a shell I81. A nose I98, slidably fittedaround the tool holder I92, is secured in the lower end of the shell I81. A contact shoe I99 correspondin'g'to the member 24, Figure 1, closely fitted around the tool I, is fastened in the lower end of the nose I 88..

A bolster plug 288 isslidably socketed in the bottom of a central hole 28l in the lower memher I 9| and ram I88, and carries a cross key 282 extending outward through lateral slots 288 in the member I9I so as to engage upward extensions 284 on the shell I91. The initial position of the shell I81 is determined by adjustment of into the hole 28 I is adapted to be screwed down-' ward to place any ,desired initial compression on the spring 2I8 by means of a squared shank 2I2 connected by bevel gears 2I3 and a shaft 2 to an exterior hand wheel 2| 5. A rotary dial 2I8, geared to the shaft 2, may be calibrated with the spring 2I8 to indicate the pressure placed thereon by the nut 2| I.

The operation of thefracture proofer is as follows:

Normally the contact shoe I88 is spaced sllghtly beyond the end of the tool I84. As the table 3| pulsates upward to apply the initial pressure as previously explained the work piece 28 first engages the shoe I99 forcing the shell I 91, cross key 282 and bolster 288 upward against the pressure of spring 2 I8 as previously determined by the setting of nut 2! I, until the tool I8! is also engaged by-the work piece. The initial upwardpressure on the tool insures extension of the tractor levers and absence of lost motion as previously explained.

As the tool I94 starts downward the part of work piece 28 surrounding thetool is held in compression due to the heavy spring 2I8. As

the tool moves through 28 the ram I88 moves downward relatively to the shell I91, key 282 and bolster plug 288. At the same time the nut 2 is carried downward by the ram, thereby further compressing the spring 2I8 and increasing the pressure applied through the shoe I59 to the piece 28. The fracture proofing pressure is thus resiliently increased from a pre-determined ini-' tial amount asthe stroke progresses, holding the portion of 28 surrounding the work area intact. The amount of pressure necessary for fracture proofing different types of work pieces having been determined, the initial adjustments of the spring 2I8 are made accordingly. If desired, the range ofthe spring may be further ,varied by the use of shims such as 2", Figure 13. The spring 2I8 may also be removed and replaced by I, another of different range.

, Clutch The clutch I36 by which power is delivered from the shaft I33 to. the high pressure linkage and to the pulsating table mechanism is preferably of the type similar to that fully described in co-pending application Serial No. 737,155 herein illustrated in Figure 17. In the above figure the numeral 2I3 indicates a driving memher secured by keys 2I9 to the shaft I33 and rotatable inside a body 223. The hub 99, to which are secured the eccentric 93, Figure 6, and crank body I39 as previously described, is formed integrally with or secured to the body 223 and is Journalled on the shaft I33 as shown in Figure 9.

The driving member 2I3 has circumferentially spaced segmental extensions 22I adapted to engage a block 222 radially slidable in the body 223 and containing a wrist pin 223. A rocking lever 224, pivoted to the body 223 at 225, has a lower arm 226 extending outwardly from 223 and carrying a contact roller 221. The upper arm 223 of lever 224 carries a pin 229 which is connected by a link 233 with the wrist pin 223. A rod 23I, slidable in a trunnion 232 mounted in the body 223, is pivotally attached to the pin 229 and is urged to the left by a spring 233. A vertical latch 234 urged upward by a spring 2340. has a lower cross bar 235 adapted to enter a notch 236 in the rod 23I. A lever 231, pivoted at 236 to the body 223 carries a trip roller 239 adapted to be engaged by the extensions 22 I and has a fork 243 spanning a roller 241 on the latch 234.

A stationary guide 242 contains a vertically slidable plunger 243 in which is vertically reciprocable a second plunger 244. A latch 245 is slidable in the plunger 243 and is urged to the left by a spring 246. The latch 246 is provided with rollers 241 venticallymoveable in slots 243 in a bell-crank 249 pivoted at 253 and connected to a vertical rod 25I having an upper inclined contact shoe 252.

The second plunger 244 has a lateral notch 253 to accommodate the end of latch 246, and is con--' a pedal 262 at the front of the base 34.

Referring again to Figure 17, the plunger 243 rests on a block 263 vertically slidable on the second plunger 244 and linked to a' lever 264 rockable on the cross shaft 265 and provided with a counter-weight 266. The cross shaft 265 pivotally supports the swinging lever I24 previously dewhich the clutch is automatically disengaged after each working operation, after which the operator removes the completed work, places a new work piece in position, then restarts themachine by engaging the clutch manually.

The operation of the clutch under these conditions is as follows:

Assuming the rotation of the shaft to be counter-clockwise, as a working cycle is completed the contact roller 221 engages a concave block 243a adjustably secured to the top of the plunger 243. The further counter-clockwise motion of the body swings the lever 224 clockwise against the spring 233, drawing down the link 233 and block 222. The block 222 is thus drawn clear of the extension 22I of the driving member which is now free to idle. As the rod 23I is forced to the right the bar 235 snaps upward into the notch 236, thus locking the block 222 in retracted position. The

roller 221 being stopped by the block 243a,. and" the clockwise swing of lever 224 being stopped bya pad 224a, the body 223 and all attached working parts of the machine are brought to rest. I

To prevent possible rebound any suitable means may be used such as a pawl 269. Figure 4, adapted to engage the bottom of crank body I39 as the latter reaches right dead center.

In order to engage the clutch manually the operator raises his foot from the pedal 262, allowing a retracting spring'213, Figure l, to swing the bell. crank 26I clockwise. The lever 251 is thereby swung toward the right, turning the cross shaft 256' to raise the second plunger 244 until the latch 245 snaps into the notch 253. The operator now depresses the pedal 262, drawing down the second plunger 244 which, being latched to the plunger 243, retracts the latter downward in the guide member 242, freeing the contact roller 221. The first of extensions 22I which thereafter engages the roller 239 throws the lever 231 downward, forcing, the cross bar 235 of latch 234 out of the notch 236. The spring 233 expands. rocking the lever 224 to the left against a second stop pad 224b, and causing the link 233 to move the block 222 upward. The succeeding extension 22I engages 222 and drives the body 223. The

machine having thus been started, the roller 221 in, sweeping counter-clockwise strikes and depresses the inclinedshoe 262, withdrawing the latch 245 from notch 263 in second plunger 244. The plunger 243 is thus released and is raised by the action of the spring 263 to its upper position.

As the body 223 completes a single revolution the contact roller 221 strikes the block 2431: to disengage the clutch and stop the machine as previously described. It'is evident from the above that the clutch automatically limits the machine to one revolution for each operation' of the foot pedal. Accidental repeating with attendant injury to operator and damage to the machine or material is thus rendered impossible.

when it is desiredto operate the machine continuously, fully automatically. as for instance when work pieces'are supplied by any suitable type of automatic feed, it is necessary that the,

clutch I36 shall remain engaged. To accomplish this end the following provision is made:

Mounted on the cross shaft 266 is a swinging lever I24 previously noted, which has a shoulder 21I adapted to engage an opposing shoulder 212 on the lever 264. The lever I24 is connected by the rod I26 and pin 213 to a lever 214 fastened to a shaft 215 as shown in Figure 12. Shaft 215 carries a similar exterior lever 216 connected by aoaassa a rod 211 to a hand lever 218 pivoted to the far side of the base 84 and having a positioning latch The latch lever 28I, pivoted at 282 and connected to the swinging lever I24 by alink 288,

contains an upwardly spring pressed latch 284 having an inclined cam face 285. As the lever I24 is swung clockwise as noted above the latch 284 is pressed against the bottom of the bell crank 249. when the inclined shoe 292 is moved downward by its flrst engagement with the contact roller 221, thus swinging the bell crank249 l to the right, the latch in is forced upward to the left of 249, the cam face 295 wedging 249 far-' ther to the right. The shoe 252 is thereby held,

clear of the roller during the succeeding revolutions of the clutch. The block 248a also remain- 5 ing lower out of range of the roller 221, the clutch remains engaged to drive the machine continuously. W

. When the machine is being operated semiautomatically as previously noted, it. is necessary 9 that the pulsating table mechanism explained in connection with Figure 6 be tripped by the same manual action by which the clutch is engaged,

as otherwise the upward pulsation occurring at the end of each return stroke would prevent un- 5 clamping and changing work pieces. For this purpose the following structure is provided:

An exterior lever 285, Figure 4, is fastened to the shaft I29 and is connected by a link 288 to an internally shouldered shell 281 containing a piston 288. The piston 289 has a rod 289 screwed into a clevis'299 pivoted to the bell crank 29L A tension spring 29I urges the lever 28! to the right.

when the pedal 262 is depressed to trip the clutch' as previously described, the lever 295 is swung to the left by the linkage just described, rocking the shaft I29 and swinging the short lever I28 to the left. The release block I21, Figure 6, is thereby moved to the left. .The spring motor is thereby tripmd and pulsates the table upward as previously described. By screwing the piston rod 289 into or out of the clevis 299 the relative tripping position of the clutch and spring motor during the actuation of the pedal may be adjusted.

Synchronizing power drive and flywheel A prime characteristic of the process of cold m flowing is extreme smoothness. To carry out the process in the most advantageous manner possible it is therefore desirable that the power be applied as smoothly as possible. As the pressure overcome by the tool and the speed at which 55 the pressure is overcome are inversely proportional, as previously set forth, the power during flow remains constant. The building up of the power from no load to-the constant power required during flow, that is theovercoming of the 7 material's elasticity, takes place at the very beginning of the-tool stroke with very low velocity. There is no peak or heavy surge of power required such as occurs in the case of a punching operation where the maximum pressure is ap- 75 plied at high velocity accompanied by shock.

7 Theoretically, therefore, no flywheel effect would be necessary for cold flowing, In practhe types disclosed in co-pendng applications Serial No. 737,162 and Serial No. 737,154 are employed to maintain a smooth flow of power directly from the prime mover'to the work, the flywheel normally doing no work on the material but serving to balance out the above described inertia effects of the'working parts.

The structures and operation of the above combination are as follows: A flywheel 292, Figure 9 and 10, is secured to a shaft 298 journalled in the side plate 494 and in a pedesta1 294 secured to an extension 289 of the base 84. vA herringbone gear 299 is also secured to the shaft 298 and is meshed with a gear 291 of larger diameter secured to the power shaft I99. A thrust bearing 298 is provided on the shaft 298 between the flywheel 292 and pedestal 294 to absorb end thrust generated due to natural weave as the flywheel, delivers'stored power to the power shaft, and a similar bearing 299 on the main shaft I99 between the g'e'ar291 and main bearing ho g 889 on the side plate 49a similarly absorbs the thrust of 29.1- whenv power is being stored in the flywheel.

A prime mover such as an electric motor 89I,-

mounted on a suitable bracket 892, is connected 4 to a shaft 898 journalled in a hous'ing894 secured to the side plate 49aby bolts 895 as shown in Figure 18. The shaft 898 carries a worm 896 meshing with a gear ring 891 secured by means of screws 898 to guide plates 899 rotatably mounted on the power shaft I99. Adriven member'8l9 is keyed to the shaft I99, and has radial' slots 8 in which are slldable inclined plungers 8II'2 retained by limiting screws 813 and urged outward by springs 8I4.

Driving blocks 8I5, slidable between the outer circumference 8I9 of the driven member 8I9 and 'the inner circumference 8I1'of the gear ring 891, are normally urged into lateral engagement with the plungers 3I2 by means of compression 5 springs 8I8 backed by inclined blwks 8I9 secured to the guide plates 899.

Power is supplied by the motor 89I, causing the worm 895 to drive the gear ring 391 clockwise, Figure 18, and, with it the guide plates 899 and inclined blocks 8I9. The driving force is transmitted through the springs 3I4 to the driv-. ing blocks 3I5 which carry around the plungers 9I2 drivihgfihe member 8I9 and power shaft I99. springs 8I8 are of such strength that in theirposition of maximum expansion, that is, with the driving blocks 8I5 stoppedby the rear ends of inclined blocks'8I8 as shown wheel 292, shaft 293 and gears 2st and 291 is made substantially equal to the combined moments of inertia of all the other working parts. When the clutch I36 is engaged, or when the ram and attached linkages reverse their directions of motion the lag or inertia of rest'is immediately balanced on by that of the moving flywheel system. In eflect, therefore, the parts start without weight, allowing the prime mover to act directly through the cushion drive to the work. This balance between the flywheel effect and inertia of the working parts is of great importance, it having been found experimentally that a greater proportionate flywheel effect produced tearing and spoiled materials while too little such effect also produced unsatisfactory work due to irregular action.

The gearing up of the flywheel through the rolling mill gears 291 and 296 gives the wheel ample energy storing capacity to perform its balancing function with small drop in speed.

In the exceptional case of sudden rises inresistance to flow due to extraordinarily hard spots or similar defects in the material being worked the flywheel supplies added working energy in the ordinary manner.

When the motor 3I'II is stopped or slows down for any reason such as current failure the driven member 3| 6 of the cushion drive mechanism,

Figure 18, overruns the gear ring 361, the plungers 3I2 reciprocating in their slots '3 as they ride forward over the inclined blocks 3I6 and driving blocks 3I5. This device thus acts as a free-wheel, protecting the worm 366 and gear 361 from destructive strain of stopping the heavy working parts. i

The action. of the complete machine may be summarized as follows:

In accordance with the size and characteristics of the work piece to be processed, the tool strokeis adjusted by means of the wheel I 41 on the micrometer crank, the initial table height is set by the hand wheel 32I, the table stroke is set.

by the hand w eel 89, the table pressure is set by the hand whee 323, and the fracture prooflng pressure is adjusted by means of the wheel 2|.

The complete working .cycle for semi-automatic operation is as follows:

l. The work piece 26 is loaded in position.

2. The pedal 262 is depressed, swinging levers 285 and to trip the pulsating table mechanism and the clutch I36.

3. The table rises, clamping the work, alining the tractor levers and insuring the high pressure linkage against lost motion. At the same time the clutch engages. v

4. The tool descends, flowing out the blank.

5. The tool withdraws upward, retractingthe fracture proofer as the upward stroke is com:- pleted. At the same time the. table is drawn downward and the spring motor is cooked.

6. The clutch automatically disengages and At the same time the table is lowered and the springmotor cocked.

5. The worked material is unloaded and replaced with a fresh blank just prior'to the next pulsation of the table.

From the foregoing it is evident that accurate timing of'the table and clutch action with respect to that of the ram is essential to proper coordination of the functions.- This is particularly true of declutching during semi-automatic operation and upward pulsation of the table during fully automatic operation. This timing is initially determined by proper angular installation of the clutch I36 and ececntric 98 with respect to the crank pin Ill. A flne timing of the clutch disengagement may be made by adjusting the contact block 243a. to right or left on the plunger 243, Figure 17. Similarly the timing of automatically tripping the spring motor may be delicately set by means-of an adjustable wedge 324, Figure 6, adapted to move the block I09 to right or left for earlier or later engagement by the trip block IIII. To provide for moving the ram by hand for testing adjustments or similar purpose a lever 32 5, Figures 4 and 15, is rotatably mounted on the cross shaft I64 and is connected by a link 326 to a socketed member 321 pivotally attached to the side plate 40 and adapted to receive a hand lever326. A tapered hole 329 is provided ex- :tending in alinzment through lever 326 and the shaft I64 when he parts are as shown in Figure 4.

' -When it is desired to move the ram by hand,

the safety shear pin IBM is removed from lever I63 and placed in the hole 326. Lever I63 is thus released from the shaft and hand lever 323 is connected to it, so that a movement of 323 acts through the high pressure linkage'to move the V ram Ill.

The invention has been described throughout particularly in its function of carrying out the method of cold flowing as set forth in application Serial Nor 702,286. However, it is also adapted to carry out the method of cold working various materials not adapted to cold flowing, for instance dissociate crystalline substances such as cast iron, as disclosed in copending application Serial No. 737,161. The machine operates on these materials in the same manner as described, but the portion 25 beneath the tool 22 instead of flowing downward as a solid plug undergoes a rapid progressive disintegration and drops out in pulverized form as fully described in the above noted application.

From the foregoing specification it is evident to those skilled in the art-that as the above cited without departing from the scope of the appended claims.

What is claimed is:

1. In a machine tool in combination, a working tool, a fracture-proofer cooperative therewith, a work table, means to puisate said table, and means to actuate said tool whereby said tool may perform a complete working stroke between complete pulsations of said table.

2. In a machine tool in combination, a working tool, a fracture proofer cooperative therewith, a work table, means to pulsate said table to bring a work piece into compressive engagement with said tool and fracture proofer and adapted to hold said table stationary during a working stroke of said tool, and means to actuate said tool in timed relation to the pulsation of said table.

3. In a machine adapted to do work on a mate rial, in combination, means to apply a pre-pressure to said material, means to map a work area in said material and to apply thereto a working .pressure decreasing in substantially parabolic relation to the increase of yield of said material, and means to maintain a compressive pressure on a portion of said material adjacent said work area. I

4. In a machine adapted to, do work on a material in combination, means to apply a pro-pressure to said material, means to map a work area in said material and to apply thereto a working pressure decreasing in substantially parabolic relation to the increase of yield of said material,

means to maintain a compressive pressure on a 'pre-pressure, and manually adjustable means to predetermine said compressive pressure.

5.' In a machine tool in combination a power shaft, a prime mover, a tool beam, a working tool associated therewith, linkage including a tractor lever adapted to transmit power from said shaft to said beam to actuate said working tool, means to transmit power from said prime mover to said shaft, and inertia means to start said linkage and beam from rest.

6. In a machine tool in combination a power shaft, a prime mover, a tool beam, a working tool associated therewith, linkage including a tractor lever adapted to transmit power from said shaft to said beam to actuate said working tool at speed increasing in substantially parabolic relation to the increase of travel thereof, means to transmit power from said prime-mover to said shaft, and inertia means to start said linkage and beam from rest.

7. In a machine tool in combination a power shaft, a prime mover, a tool beam, a working tool associated therewith, linkage including a tractor lever adapted to transmit power from saidshaft to said beam to actuate said working tool, means to transmit power from said prime mover to said shaft, inertia means to start said linkage and said beam whereby said working tool may be.

actuated, means to transmitpower from said prime mover to said shaft, inertia means to start said linkage and beam from rest, a worktable, means-operable by said shaft through clutch to pulsate said table, automatic means to disengage said clutch, and manual means to .engage said clutch and actuate said pulsating means.

9. In a machine tool in combination, a power shaft,'a clutch on said shaft, a prime mover, a tool beam, a working tool associated therewith, linkage including a tractor lever adapted to transmit power from said shaft through said clutch to said beam whereby said working tool may be actuated, means to transmit power from said prime mover to said shaft, inertia means to start said linkage and beam from rest, a work table, means operable by said shaft through said clutch to pulsate said table in timed relation to the actuation of said working tool, automatic means to disengage said clutch in timed relation to the actuation of said working tool, and manual means to engage said clutch and actuate said pulsating means.

10. In a machine tool in combination a power shaft, a prime mover, a-too1 beam, a working tool associated therewith, linkage including a tractor by said shaft to pulsate said table, manual meansto vary the stroke of said working tool, manual means to vary the amplitude of pulsation of said table, and manual means to adjustably predetermine the power of said pulsation.

11. In a machine tool in combination a power shaft, a prime mover, a 'tool beam, a working tool vassociated therewith, linkage including a tractor lever adapted to transmit power from said shaft to said beam to actuate said working tool, resilient means including a free wheel to transmit power from said prime mover to said shaft, and inertia means to start said linkage and beam from rest.

12. In a machine adapted to produce cold flow in a material, means to apply a pre-pressure to said material in one direction, means to apply a working force to said material in the oppositedirection, and means to maintain a portion of said material under fracture proofing compressive pressure during the application of said workingforce. 13. In a machine adapted. to produce cold flow in a-material, a tool, actuating means including a tractor lever associated with'said tool, means to apply a pre-pressure through said material and tooito said actuating ,means whereby said tractor lever may be placed in infinite plane condition, means to actuate .said tractor lever. by 'rupture of said infinite plane condition to apply a working force through said tool to said material, and means to preserve said material from fracture.-

14. In a machine adapted-to produce cold flow in a material, means to apply a pre-pressure of said material under fracture .prooflng compressive pressure during theapplication of said working force.

cnsnnas n. ROWLAND-mm. 

